EP1971815B1 - Spiralförmig gewickelter, geschichteter rohrwärmetauscher - Google Patents

Spiralförmig gewickelter, geschichteter rohrwärmetauscher Download PDF

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Publication number
EP1971815B1
EP1971815B1 EP06840299A EP06840299A EP1971815B1 EP 1971815 B1 EP1971815 B1 EP 1971815B1 EP 06840299 A EP06840299 A EP 06840299A EP 06840299 A EP06840299 A EP 06840299A EP 1971815 B1 EP1971815 B1 EP 1971815B1
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EP
European Patent Office
Prior art keywords
layers
heat exchanger
exchanger assembly
tube
tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06840299A
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English (en)
French (fr)
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EP1971815A4 (de
EP1971815A2 (de
Inventor
Olli Pekka Naukkarinen
Hailing Wu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Modine Grenada LLC
Original Assignee
Luvata Grenada LLC
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Publication date
Application filed by Luvata Grenada LLC filed Critical Luvata Grenada LLC
Publication of EP1971815A2 publication Critical patent/EP1971815A2/de
Publication of EP1971815A4 publication Critical patent/EP1971815A4/de
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Publication of EP1971815B1 publication Critical patent/EP1971815B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • F28D1/0473—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0132—Auxiliary supports for elements for tubes or tube-assemblies formed by slats, tie-rods, articulated or expandable rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators

Definitions

  • This invention relates generally to a heat exchanger assembly according to the preamble of claim 1.
  • a heat exchanger assembly is known from FR 2128127 .
  • thermal energy is transferred from one location to another or from one fluid to another.
  • Heat exchangers allow the transfer of heat from one fluid (liquid or gas) to another fluid.
  • the reasons for transferring heat energy are:
  • the heat exchanger fulfills, in order to transfer heat, the fluids in thermal contact must be at different temperatures to allow heat to flow from the warmer to the cooler fluid according to the second principle of thermodynamics.
  • HVAC heating, ventilation, air conditioning and refrigeration
  • All air conditioning and refrigeration systems contain at least two heat exchangers - usually an evaporator and a condenser.
  • the refrigerant flows into the heat exchanger and participates in the heat transfer process, either gaining or releasing it to the medium to be used.
  • the cooling medium is air or water.
  • a condenser accomplishes this by condensing the refrigerant vapor into a liquid, transferring its phase change (latent) heat to either air or water.
  • the liquid refrigerant flows into the heat exchanger. Heat flow is reversed as refrigerant evaporates into a vapor and extracts heat required for this phase change from the hotter fluid flowing on the other side of the tubes.
  • Tubular heat exchangers include those used in an automotive heat exchanger environment, such as a radiator, a heater coil, an air cooler, an intercooler, an evaporator and a condenser for an air-conditioner.
  • a hot fluid flows internally through pipes or tubes while a cooler fluid (such as air) flows over the external surface of the tubes.
  • Thermal energy from the hot internal fluid is transferred by conduction to the external surface of the tubes. This energy is then transferred to and absorbed by the external fluid as it flows around the tubes' outer surfaces, thus cooling the internal fluid.
  • the external surfaces of the tubes act as surfaces across which thermal energy is transferred.
  • longitudinal or radial fins may be positioned in relation to the external surface of the tubes to turbulate the externally flowing fluid, increase the area of the heat transfer surface and thus enhance the heat transfer capacity.
  • fins add to material and manufacturing cost, bulk, handling, servicing and overall complexity. Further, they occupy space and therefore reduce the number of tubes that can fit within a given cross sectional area. Also, they collect dust and dirt and may get clogged, thereby diminishing their effectiveness.
  • Densely configured external fins tend to constrict external fluid flow. This increases the pressure drop of the external fluid across the heat transfer surface and may add to heat exchanger costs by requiring more pumping power. In general, expense related to pumping is a function of the pressure drop.
  • Fin-less, tube heat exchangers are known. See, e.g., U.S.P.N. 5,472,047 (Col. 3, lines 12-24). Conventionally, however, they are made of tubes having a relatively large outside diameter. Often, tubes are joined with wires, such as the steel coils found at the back of many residential refrigerators.
  • US 4,108,420 describes a heat exchanger system for heat exchange between a gas such as air and a liquid such as water.
  • the heat exchanger system has at least one heat exchanger unit which comprises at least one tube wound to form a hollow coil which is arranged to conduct the liquid.
  • the coil is closed or covered at one end, the other end of the coil is open and is placed against the base plate having an opening which is aligned with the coil opening and has a size and shape corresponding to those of the coil opening.
  • the turns of the coil are slightly separated in order to permit gas flow perpendicularly across the tube during passage through the wall of the coil.
  • FR2128127 describes a fluid heat exchanger comprising chamber in which one fluid circulates inside a stack of metallic tubes and another fluid circulates around the tubes; and a collector for admission and evacuation of fluids to/from the tubes, wherein the stack consists of a stacking of spiral tubes in which each tube forms a spiral such that the spacing between successive coils of the spiral is at least equal to the outer diameter of the tube, the spiral beings stacked coaxially in a fashion to form an assembly
  • Embodiments provide a uniformity of flow of external heat exchange fluid across layers of tube and between tubes in a layer within which an internal heat exchange fluid passes, thereby avoiding areas of stagnation that reduce the efficiency of the heat exchange process.
  • Embodiments provide a heat exchanger that can be made relatively inexpensively and efficiently without requiring undue complexity in the manufacturing process.
  • a heat exchanger is described that transfers thermal energy between an internal heat exchange fluid that flows within the tubing and an external heat exchange fluid in thermal communication with the internal heat exchange fluid.
  • the heat exchanger includes one or more layers of a tube within which the internal heat exchange fluid passes. At least some of the one or more layers has a spiral configuration with at least some segments that lie on an imaginary frustoconical surface.
  • At least one spacer member supports one or more of the layers.
  • Each spacer member has forwardly and rearwardly facing edges. Those edges define engagement surfaces which detachably retain tubes in the layers.
  • Figures 1-4 respectively depict a side and axial cross sectional view of preferred and alternate embodiments of a heat exchanger assembly 10.
  • the assembly transfers thermal energy between an internal heat exchange fluid 12 that flows within the exchanger and an external heat exchange fluid 14 (such as but not limited to an air flow) that is in thermal communication with the internal heat exchange fluid 12.
  • the fluids 12, 14 could be gas, liquid or gas-liquid in any combination.
  • the heat exchange assembly 10 includes one or more layers of tube or tubing 16 ( Figure 2 ) within which the internal heat exchange fluid 12 passes. At least some of those layers preferably have a spiral configuration, as depicted in Figures 1-2 . In that spiral configuration, at least some segments 20 lie on an imaginary frustoconical surface.
  • the term “spiral” includes but is not limited to a three-dimensional curve that turns around an axis at a continuously varying distance while moving parallel to the axis. It will be appreciated that the rate of change of the continuously varying distance may be constant or variable so as to produce a more or less accentuated spiral form, depending on the thermodynamic requirements of a particular application. As used herein, the term “spiral” includes the term "helix”.
  • the layers of tubing are characterized by an inter-layer spacing S and an average distance d from a tube center to the center of an adjacent tube ( Figure 2 ).
  • Distance d can be either fixed, variable, or a combination of fixed and variable within a given layer.
  • the dimension d is equal to or less than twice the average outside diameter of tubing.
  • the dimension (S) can be fixed, variable, or a combination of fixed and variable between the layers in a given configuration.
  • S is less than 2 x OD.
  • a spacer member 24 ( Figure 5 ) supports one or more of the one or more layers so that the dimensions S and d can be pre-defined.
  • Each spacer member has a forwardly and rearwardly facing edge 26,28 (in relation to the flow of external heat exchange fluid).
  • the edges 26,28 define engagement surfaces 30 that detachably retain the layers 16.
  • the forwardly facing edges 26 may retain segments of one layer while the rearwardly facing edges 28 retain segments of an adjacent layer.
  • the engagement surfaces 30 comprise a truncated form having an open portion 38 that is sized less than the outside diameter (OD) of the tube.
  • an elongate spacer member 24 defines engagement surfaces 30 that detachably retain segments 20 of the tubing.
  • the engagement surfaces 30 are defined within the forwardly 26 and rearwardly 28 facing edges.
  • the forwardly facing edge 26 detachably retains one run of one revolution 32 of the spiral configuration 15.
  • the rearwardly facing edge 28 detachably retains a run of an adjacent layer.
  • spacer members 24 may be provided within the same heat exchanger.
  • the spacer members 24 may or may not be parallel with each other and may or may not extend perpendicularly in relation to the layers 16.
  • spacer member 24 supports the three-dimensional shape of the tube heat exchanger. Although one spacer member 24 is depicted in Figure 5 , it will be appreciated that other spacer members could additionally be deployed within a given heat exchanger. Additional spacer members 24 could for example, serve to deflect air flow advantageously so that the predominant air flow occurs through the central regions of the heat exchanger where certain coil segments run in close parallel proximity. Also, the spacer member 24 may serve as a thermal communication member between tubes and layers.
  • the tube has an average outside diameter (OD), an average inside diameter (ID) and an average wall thickness (T).
  • OD average outside diameter
  • ID average inside diameter
  • T average wall thickness
  • (T ID - ID)/2.
  • the ratio of (T) to (OD) is between 0.01 and 0.1.
  • the heat exchanger has one or more layers 16 of discrete tubing or tubes (one per layer), or a single, long, continuous, tube. It will be appreciated that the tube need not be circular or annular in cross section.
  • the tube may usefully have an oval configuration or other non-circular cross section which may be helpful in directing incident air flow ("external heat exchange fluid", 14) with less pressure loss and/or promoting local turbulence.
  • Tubes may contain multiple ports.
  • a given tube may contain multiple passages or lumens.
  • At least some of the one or more layers 16 have a circular, an ovate, oblong, or racetrack-like spiral configuration 18 ( Figures 1-2 ).
  • a heat exchanger assembly is contemplated by the present invention.
  • the assembly includes the spiral configuration of tube heat exchanger ( Figures 1-4 ), at least one spacer member, a leading nose 46 ( Figures 1 and 2 ), a guiding baffle 48 ( Figures 2-4 ), and a blower 62 ( Figure 3 ).
  • the depicted spiral configuration ( Figures 1-4 ) is one example of a contoured configuration.
  • the contoured configuration may have a circular axial cross section (instead of the frusto-conical spiral configuration depicted in Figure 2 ), a triangle, a rectangle, a polygon, an oval, an oblong, an ellipse, and combinations thereof.
  • the spacer members are provided with a geometry appropriate to the form desired.
  • the spacer members 24 position adjacent tube layers.
  • Detents or engagement surfaces 30, preferably frusto-circular if round tubes are used, are defined within edges 26,28 of the spacer.
  • detents 30 terminate at the spacer edges in a position that is slightly offset from a major diameter of a detent, which may be circular, or non-circular. In this way, the outside diameter of a tube segment is engaged by a snap fit within the spacer.
  • the distance between consecutive detents (d) (center-to-center of the grooves) influences one heat transfer characteristic of the heat exchanger. In one preferred embodiment, this distance is twice the outside diameter (OD) of the tube.
  • At least some of the one or more layers include tubes with centers that lie on the same imaginary line, as suggested in Figure 2 .
  • the tubes of every second layer may lie on the same line with various offsets compared to tubes of adjacent layers.
  • the velocity of external heat exchange fluid 16 that passes through a central region of the layers 16 would conventionally exceed the velocity at which external heat exchange fluid 14 traverses the layers toward their upper right hand - and lower left hand (as seen in Figure 7 ) areas.
  • the inter-tube spacing (d) in a given layer and the inter-layer spacing (S) in a given configuration can be adjusted. As a result of the adjustment, barriers to flow, which causes stagnancy in adjacent area, may be eased.
  • Tubes may contain multiple ports (as noted earlier), and/or may be enhanced with internal or external surface microstructures, such as but not limited to grooves or a grain texture.
  • a method is described of making such a heat exchanger.
  • the method comprises the steps of providing an elongated mandrel.
  • the mandrel has an outside surface in which one or more continuous helical grooves are defined.
  • the tube becomes accommodated by the helical groove.
  • the mandrel preferably is cone-shaped.
  • a continuous length of a tube is then wound around the mandrel so as to prepare the windings, each winding having a spiral configuration.
  • Figure 2 depicts an alternate embodiment heat exchanger in which there are multiple layers.
  • the innermost coil is first formed on a mandrel or spacer member 24 ( Figure 5 ).
  • An outer layer is then wound around on top of it. Positioning of adjacent coils in a given layer and between the layers themselves is enabled by a selection of suitable spacer geometry.
  • the tube diameter in an innermost layer may differ from that found in an outermost layer. In such embodiments, it is preferable that the outside diameter of the innermost tube layers exceeds that found in the outermost tube layers.
  • the spacer member 24 itself may assume the function of a mandrel. In such cases, a length of tubing is wound around the spacer. It will be appreciated that a given spacer member may itself be solid, or hollow. One example is that of a spacer formed by a pair of plates that are separated by an interstitial support member. Optionally, the mandrel may contain the spacers prior to winding.
  • a leading nose 46 is presented to the external heat exchange fluid 14.
  • the leading nose 46 extends ahead of the spiral configuration 18 of layer 16.
  • a guiding baffle 48 ( Figure 2 ) is positioned in relation to the layer 16 so that it directs the flow of the external heat exchange fluid between the tubes in a layer and between layers in the one or more layers of tubing.
  • a planar region of layers 49 is juxtaposed between the leading nose 46 and at least some of the one or more layers have a spiral configuration 18.
  • Figure 4 depicts a second alternate embodiment of the invention.
  • a cylindrical region 50 of layers is juxtaposed between the spiral configuration 18 and the guiding baffle 48.
  • FIGS 1-2 depict bundles of coiled tubing that serve as a heat exchanger having a spiral configuration 18 in a heat exchanger assembly 10. Noteworthy in the embodiment depicted is the absence of fins or louvers (with the exception of spacer members) that are often used in heat exchangers to promote air flow and thus the efficiency of thermal energy transfer.
  • a heat exchanger fluid enters a coiled tube at an inlet.
  • the incoming fluid is a refrigerant or another liquid such as water that is suitable for heat transfer.
  • the water could be introduced at a relatively high temperature.
  • the heat exchanger serves to elevate the temperature of a fluid such as air that passes around and outside the coiled tubes.
  • the heat exchanger effectively is a wound layered tube apparatus. Hence, it is less expensive to manufacture and maintain than conventional round tube plate fin heat exchangers.
  • internal fluid distributors may be used to distribute the internal fluid into multi-inlets and collect the fluid from multi-outlets.
  • the spacer member 24 ( Figure 5 ) is formed from a deformable material primarily to accommodate a snap fitting engagement with the tubing.
  • the spacing member 24 may be formed from a heat conducting or insulating material. If so, heat may be transferred efficiently between tube surfaces, or isolated between the two.
  • the heat exchanger tubes can be made from any heat-conducting material. Metals, such as copper or aluminum are preferred, but plastic tubes having a relatively high thermal conductivity or a thin wall may also be used.
  • the tube inside diameter (ID), outside diameter (OD), and wall thickness (T) are somewhat limited by the manufacturing techniques used to form the tube. Clearly, the selection of suitable dimensions will influence the pressure-bearing capability of the resulting heat exchanger. In general, it can be stated that as the outside diameter (OD) decreases, the thinner the wall section (T) can be. Preferably, the outside diameter (OD), inside diameter (ID) and thus wall thickness (T) are selected so that the tube can hold the pressure of an internal heat exchange fluid without deformation of the tube material. When the outside diameter decreases, the ratio of tube outer surface over internal volume of the tube increases. As a consequence, there is more heat transfer area per internal fluid volume.
  • the spacer member 24 prevents tube migration.
  • the spacing of detents 30 within the spacer member 24 is such as to cause the runs of consecutive layers to lie closely together or be spaced apart. This results in a control over packing density that influences resistance to the flow of external heat exchange fluid, local turbulence, laminar flow, and consequent management over the efficiency of heat transfer.
  • Figures 1 and 2 could be connected in series or parallel. Parallel configurations could be helpful when more capacity is needed. Such configurations may be advantageous where a long tube length may cause too high of a pressure drop and thus internal fluid flow is limited. In such arrangements it may be useful to use fluid distributors to provide the distribution of internal fluid flow to inlets and the confluence from outlets.

Claims (14)

  1. Wärmeaustauscheranordnung, die Folgendes umfasst:
    eine vordere Nase (46), die einem externen Wärmeaustauschfluid (12) ausgesetzt ist;
    eine oder mehrere Schichten (16) eines Rohrs, in dem sich ein internes Wärmeaustauschfluid (12) bewegt, wobei wenigstens einige der einen oder der mehreren Schichten eine schraubenlinienförmige Konfiguration (18) haben, wobei wenigstens einige Segmente auf einer imaginären kegelstumpfförmigen Oberfläche liegen; und
    eine Führungsablenkplatte (48), die in Bezug auf die eine oder die mehreren Schichten des Rohrs so positioniert ist, dass die eine oder die mehreren Schichten (16) zwischen der vorderen Nase und der Führungsablenkplatte nebeneinander liegen, wobei die Führungsablenkplatte dazu dient, die Strömung des externen Wärmeaustauschfluids zwischen Rohren in einer Schicht und Zwischenschichten in der einen oder den mehreren Schichten der Verrohrung zu leiten,
    wobei sich die imaginäre kegelstumpfförmige Oberfläche von ihrem kleinen Ende zu ihrem gegenüberliegenden großen Ende konisch erweitert, dadurch gekennzeichnet, dass sich wenigstens ein Abschnitt der vorderen Nase über das kleine Ende der imaginären kegelstumpfförmigen Oberfläche hinaus erstreckt.
  2. Wärmeaustauscheranordnung nach Anspruch 1, wobei wenigstens einige der einen oder der mehreren Schichten (16) eine angepasste Konfiguration haben,
    wobei die Anordnung Folgendes umfasst:
    ein oder mehrere Abstandshalterelemente (24), die eine oder mehrere der Schichten (16) tragen, wobei das eine oder die mehreren Abstandshalterelemente nach vorn und nach hinten weisende Kanten besitzen, wobei die Kanten Eingriffoberflächen definieren, die die Schichten lösbar halten; und
    ein Gebläse (62), um eine Strömung des externen Wärmeaustauschfluids zu fördern.
  3. Wärmeaustauscheranordnung nach Anspruch 2, wobei die angepasste Konfiguration einen Querschnitt besitzt, der eine Form hat, die aus der Gruppe ausgewählt ist, die besteht aus einem Kreis, einem Dreieck, einem Rechteck, einem Polygon, einem Oval, einer Langform, einer Ellipse und Kombinationen hiervon.
  4. Wärmeaustauscheranordnung nach Anspruch 1, wobei eine der einen oder der mehreren Schichten (16) des Rohrs gekennzeichnet ist durch eine Strecke d von einem Rohrzentrum zu einem Zentrum eines benachbarten Rohrs in derselben Schicht, wobei d eine Abmessung ist, die aus der Gruppe gewählt ist, die besteht aus festen und variablen Werten sowie aus Kombinationen aus festen und variablen Werten, wobei d vorzugsweise gleich oder kleiner als der doppelte mittlere Außendurchmesser, OD, des Rohrs ist.
  5. Wärmeaustauscheranordnung nach Anspruch 1, wobei ein durchschnittlicher Zwischenraum, S, zwischen benachbarten Schichten (16) in wenigstens einigen der einen oder der mehreren Schichten eine Abmessung ist, die aus der Gruppe gewählt ist, die aus festen und variablen Werten und aus Kombinationen hiervon besteht.
  6. Wärmeaustauscheranordnung nach Anspruch 5, wobei S kleiner als 2 × OD ist.
  7. Wärmeaustauscheranordnung nach Anspruch 6, wobei wenigstens einige der einen oder der mehreren Schichten Rohre enthalten, deren Zentren auf derselben Linie liegen.
  8. Wärmeaustauscheranordnung nach Anspruch 6, wobei Rohre jeder zweiten Schicht auf derselben Linie liegen.
  9. Wärmeaustauscheranordnung nach Anspruch 1, wobei eine der einen oder der mehreren Schichten (16) eine Rohrstrangkonfiguration hat, die aus einem Einlass und einem Auslass besteht.
  10. Wärmeaustauscheranordnung nach Anspruch 1 oder 9, wobei eine der einen oder der mehreren Schichten eine Rohrstrangkonfiguration besitzt, die aus einem Einlass und einer Auslaufverbindung mit einer benachbarten Schicht besteht.
  11. Wärmeaustauscheranordnung nach Anspruch 1, 9 oder 10, wobei eine der einen oder der mehreren Schichten eine Rohrstrangkonfiguration besitzt, die aus einem Auslass und einer Einlaufverbindung mit einer benachbarten Schicht besteht.
  12. Wärmeaustauscheranordnung nach Anspruch 1, wobei das Rohr ein Querschnittsprofil besitzt, das aus der Gruppe gewählt ist, die aus einem Kreis, einem Oval, einer Ellipse, einem Rechteck mit abgerundeten Ecken und Kombinationen hiervon besteht.
  13. Wärmeaustauscheranordnung nach Anspruch 1, die ferner einen ebenen Bereich von Schichten (49) umfasst, der zwischen der vorderen Nase (46) und wenigstens einigen der einen oder der mehreren Schichten mit einer schraubenlinienförmigen Konfiguration (18) nebeneinander liegt.
  14. Wärmeaustauscheranordnung nach Anspruch 13, die ferner einen zylindrischen Bereich (50) von Schichten aufweist, der zwischen der schraubenlinienförmigen Konfiguration (18) und dem Führungsablenkblech (48) liegt.
EP06840299A 2005-12-21 2006-12-18 Spiralförmig gewickelter, geschichteter rohrwärmetauscher Not-in-force EP1971815B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/315,108 US7546867B2 (en) 2004-11-19 2005-12-21 Spirally wound, layered tube heat exchanger
PCT/US2006/062217 WO2007076314A2 (en) 2005-12-21 2006-12-18 Spirally wound, layered tube heat exchanger and method of manufacture

Publications (3)

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EP1971815A2 EP1971815A2 (de) 2008-09-24
EP1971815A4 EP1971815A4 (de) 2009-06-10
EP1971815B1 true EP1971815B1 (de) 2013-02-20

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EP06840299A Not-in-force EP1971815B1 (de) 2005-12-21 2006-12-18 Spiralförmig gewickelter, geschichteter rohrwärmetauscher

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US (1) US7546867B2 (de)
EP (1) EP1971815B1 (de)
CN (1) CN101379358B (de)
MX (1) MX2008008179A (de)
WO (1) WO2007076314A2 (de)

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Also Published As

Publication number Publication date
MX2008008179A (es) 2009-01-26
WO2007076314A2 (en) 2007-07-05
CN101379358B (zh) 2013-08-07
EP1971815A4 (de) 2009-06-10
CN101379358A (zh) 2009-03-04
EP1971815A2 (de) 2008-09-24
US7546867B2 (en) 2009-06-16
WO2007076314A3 (en) 2007-12-27
US20060108108A1 (en) 2006-05-25

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